US4795131A - Vacuum controller - Google Patents

Vacuum controller Download PDF

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Publication number
US4795131A
US4795131A US06/922,521 US92252186A US4795131A US 4795131 A US4795131 A US 4795131A US 92252186 A US92252186 A US 92252186A US 4795131 A US4795131 A US 4795131A
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US
United States
Prior art keywords
piston
vacuum
valve
valve piston
sub
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US06/922,521
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English (en)
Inventor
Robert V. Scarano
Joseph A. Bolton
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kadant Inc
Original Assignee
Albany International Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Albany International Corp filed Critical Albany International Corp
Assigned to ALBANY INTERNATIONAL CORPORATION reassignment ALBANY INTERNATIONAL CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: BOLTON, JOSEPH A., SCARANO, ROBERT V.
Priority to US06/922,521 priority Critical patent/US4795131A/en
Priority to IT4816487A priority patent/IT1218140B/it
Priority to AU75987/87A priority patent/AU588706B2/en
Priority to FI873301A priority patent/FI85621C/fi
Priority to NL8701851A priority patent/NL8701851A/nl
Priority to JP20940487A priority patent/JPH073270B2/ja
Priority to CA 545528 priority patent/CA1290308C/en
Priority to DE19873733673 priority patent/DE3733673C2/de
Priority to AT267687A priority patent/AT389178B/de
Priority to FR8714252A priority patent/FR2609563B1/fr
Priority to SE8704084A priority patent/SE467546B/sv
Priority to BE8701208A priority patent/BE1001002A5/fr
Priority to NO874427A priority patent/NO172004C/no
Priority to GB8724876A priority patent/GB2197935C/en
Publication of US4795131A publication Critical patent/US4795131A/en
Application granted granted Critical
Assigned to THERMO FIBERTEK INC. reassignment THERMO FIBERTEK INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ALBANY INTERNATIONAL CORP.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/1223—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being acted upon by the circulating fluid
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/14—Control of fluid pressure with auxiliary non-electric power
    • G05D16/18—Control of fluid pressure with auxiliary non-electric power derived from an external source
    • G05D16/187—Control of fluid pressure with auxiliary non-electric power derived from an external source using pistons within the main valve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S137/00—Fluid handling
    • Y10S137/907—Vacuum-actuated valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86718—Dividing into parallel flow paths with recombining
    • Y10T137/86734—With metering feature
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86718—Dividing into parallel flow paths with recombining
    • Y10T137/86759—Reciprocating
    • Y10T137/86791—Piston

Definitions

  • the present invention relates to a vacuum controller, in particular, a vacuum controller which automatically controls the vacuum supplied.
  • valves used to control the vacuum being supplied at a particular application In particular, in the papermaking industry vacuum control valves are used extensively. In a typical situation such valves are used to regulate the suction to the suction boxes. See, for example, U.S. Pat. No. 3,766,933.
  • An automatic valve of this nature which has been widely utilized is that sold by Albany International, assignee herein, under Model No. AES V-700.
  • the V-700 valve which is basically shown in FIG. 1, utilizes two back-to-back piston assemblies with different size pistons and rolling diaphragms.
  • U.S. Pat. No. 4,413,644 shows a bleeder valve comprising a plurality of valve members in tandem to control the vacuum in suction boxes and the like.
  • U.S. Pat. No. 4,390,036 provides for a vacuum controller which utilizes several plungers, one of which has several openings in its inside wall which utilizes a rolling diaphragm to close off or open access to the vacuum source and/or the atmosphere for throttling purposes, etc.
  • U.S. Pat. No. 4,466,455 relates to a vacuum controller which uses a reciprocal plunger and flexible diaphragm which operates as a valving mechanism. As the plunger moves one way, the diaphragm closes off the opening in the side wall of the plunger and in the opposite direction it opens the opening.
  • the present invention provides for a vacuum controller which utilizes a balance piston design for controlling a regulated vacuum chamber such as that coupled to the flat box section of a papermaking machine.
  • a cavity exists between a large upper piston and diaphragm on a small lower piston.
  • the diaphragm is pressurized with compressed air which will tend to lift the assembly due to the difference in the piston areas.
  • the bottom of the lower piston is exposed to the regulated or controlled vacuum provided, for example, to the flat boxes which pulls the assembly downward.
  • the compressed air signal is adjusted to generate a force equal to the force generated by the effect of the controlled vacuum on the bottom of the lower piston.
  • the entire piston assembly is free to move vertically to a location where the forces involved are balanced.
  • Throttling is accomplished through the use of a vertical window of a constant diameter and varying height.
  • the bottom piston is exposed to only controlled vacuum and not the average of the header or source vacuum and controller vacuum.
  • the use of a larger (variable) throttling passage avoids the clogging of throttling holes.
  • the use of a lighter diaphragm is possible which allows for flexibility and quicker response time.
  • the shape of the piston may be varied as long as the control area, that area upon which the controlled or regulated vacuum acts, is maintained by the geometry of the valve so that the header or source vacuum does not migrate under the piston and thereby influence the control of the piston.
  • the balancing piston may include a plurality of pistons operating in tandem for the particular balancing needs and may also include a feedback means to allow for self-adjusting of the valve.
  • FIG. 1 is a sectional view of a vacuum controller in the prior art
  • FIG. 2 is a sectional view of a vacuum controller incorporating the teachings of the present invention
  • FIG. 3A is an enlarged partially sectional view of a modified version of a vacuum controller with its plunger in a mid-way position, incorporating the teachings of the present invention
  • FIG. 3B is a view similar to FIG. 3A with, however, the plunger shown in a fully closed position;
  • FIG. 3C is a view similar to FIGS. 3A and 3B with, however, the plunger shown in a fully open position;
  • FIG. 4 is an enlarged view of a vacuum controller similar to FIGS. 3A-3C, however, having two balancing pistons, incorporating the teachings of the present invention.
  • FIG. 2 there is shown a vacuum control valve or controller 10 which includes a cylindrical outer casing 12 in which a valve member 14 reciprocates.
  • the controller 10 is coupled to a source header vacuum through conduit 16 and, for example, a separator and regulated or controlled vacuum at, i.e., flat boxes through conduit 18.
  • the valve member 14 includes two pistons the first piston 20 of which is larger then the second piston 22 coupled by a shaft member 24 such that the pistons 20 and 22 move in tandem.
  • Each piston 20 and 22 is provided with rolling diaphragms (upper) 26 and 28 (lower), respectively, which define chambers 30 and 30A.
  • the lower diaphragm 26 rides between the piston 22 and a downwardly extending continuous sleeve 34.
  • Piston 22 is positioned above a circular valve seat or ring 32 which, with the piston 22, serves to define a chamber 36 in which conduit 16 communicates.
  • Chamber 30A may be at atmospheric with chamber 30 communicating with a source of control pressure via inlet 38. An increased pressure in chamber 30 will tend to lift the valve assembly 14. The bottom 40 of the lower piston 22 is exposed to the controlled or regulated vacuum which tends to pull the assembly downward.
  • the control air signal at 38 can be adjusted to generate a force equal to the force generated by the effect of the desired control vacuum on the bottom 40 of the lower piston 22.
  • the entire piston assembly is free to move vertically to a location where the forces involved are in balance.
  • Throttling is accomplished through the use of a vertical window of constant diameter and varying height. This would be the smallest distance between the valve seat or ring 32 and the bottom 40 of the piston 22.
  • the piston 22 should not be allowed to travel to such a great extent that the throttling point extends beyond the bottom 40 of piston 22 which would allow the higher header vacuum to migrate under the bottom 40. If that were to occur, this would lead to the undesired result that the header vacuum would influence the control of the piston assembly 14.
  • piston 22 While a cylindrical flat bottom piston 22 is shown wherein the throttling takes place between the valve seat 32 and the edge 42 of piston 22, other shapes and sizes of pistons may be utilized as long as throttling zone is controlled such that the header vacuum does not migrate to influence movement of the piston assembly 14. Arrangements such as tapered pistons and tapered valve seats may also be used if suitable for purpose.
  • FIGS. 3A-3C there is shown a somewhat enlarged vacuum controller valve 100 coupled to a separator 102 via a stand pipe 104.
  • the stand pipe 104 is typically coupled to a flat box used in papermaker applications and a source of controlled or regulated vacuum.
  • the vacuum controller 100 is also coupled via a conduit 106 to a source of vacuum or vacuum header.
  • an air regulator 108 is utilized such as that provided by Albany International, assignee hereof in its AES-700 Control System Regulator, whose function will be discussed.
  • the vacuum controller 100 comprises a balance piston assembly 110 which utilizes air pressure from a regulator 108 to feed a low friction air cylinder 112 which serves to counteract or adjust for the force acting against the valve plug or piston 114, by the controlled vacuum as will also be discussed.
  • the air cylinder 112 comprises an air piston 116 which slideably reciprocates in a cylinder 118 defining two chambers, one upper 120 and low 122.
  • Chamber 120 is at atmospheric pressure via port 124 with chamber 122 coupled to the regulator 108 via port 126 so that the desired variation of pressure in chamber 122 as regulated by regulator 108 will result in a force exerted on the piston 116 and allow for a variation of vacuum as desired.
  • Piston 116 is coupled to piston 114 by way of a rod 128.
  • Piston 114 is subject to vertical movement within a cylindrical valve wall 130 at its upper end defining a chamber 132 which is vented to the atmosphere via ports 134.
  • valve ring or seat 136 is provided in which piston 114 reciprocates.
  • Chamber 137 which is intermediate the valve wall 130 and valve ring 136 communicates with conduit 106.
  • the position of the piston 114 with respect to the valve ring determines the flow from the suction or flat box up the separator 104 through the valve ring 136 and out the side of the controller 100 to the vacuum header via conduit 106.
  • FIG. 3A the position of the piston 114 is shown in its mid-way or half open position.
  • the bottom of the piston 114 is provided with V-shaped notches 138 about its circumference through which the flow passes.
  • other shaped pistons suitable for purpose may also be utilized.
  • FIG. 3B shows the piston 114 in the fully closed position so that no flow passes with FIG. 3C showing it in a fully open position where maximum air flow exists.
  • the basic operation of the controller 100 is as follows.
  • the regulator 108 is used in association with the air cylinder 112 to counteract the force acting against the piston 114 or otherwise adjust its position to vary the vacuum being supplied.
  • the downward force acting against the piston 114 is due to the pressure differential across it with atmospheric pressure on top in chamber 120 and the controlled or regulated vacuum on the bottom in the conduit 140 coupled to the stand pipe 104.
  • the air pressure to chamber 122 is increased which increases the upward force acting on the piston 116 and in turn piston 114.
  • the piston 114 moves upward increasing the exposed open areas of the V-notches, reducing the pressure differential across the piston 114 resulting in a higher vacuum at the stand pipe.
  • Piston 114 moves upward until the downward forces acting on the valve plug or piston 114, due to the control vacuum, equal the upward force provided by the air cylinder 112.
  • the header vacuum P 4 plays no part in the operation of the controller. This is important because the controlled or regulated vacuum would vary if the header vacuum changed.
  • the controlled vacuum 5" Hg or 2.5 ⁇ psi.
  • the converting or unbalanced force on the valve can be determined as follows:
  • the unbalanced or correcting force is acting upward with a force of 11.2 lbs. pushing the valve, plug or piston 114 up to allow for more open area, thereby trying to get the vacuum back to its controlled vacuum of 5" Hg.
  • FIG. 4 there is shown a tandem arrangement for the low friction air cylinder with like parts similarly numbered but designated with a prime'.
  • the air cylinder 112' now comprises a double piston arrangement 142 and 144 with respective piston rods 146 and 148 all of which couple to piston 114'.
  • Four chambers 120', 150, 122' and 152 are now formed in the air cylinder 112' with the former two and latter two operating in tandem on their respective pistons.
  • the weight of the piston assembly (piston 142, 144, rods 146, 148) is now assumed to be 6 lbs. instead of 3 lbs. as with the single air cylinder and valve, plug or piston 114' still weighs 5 lbs.
  • the vacuum controller 112 may include a feedback means 154 which couples chamber 152 to the stand pipe 104 or conduit 140. This provides a feedback or self-correcting feature between P 4 and P 7 . If P 7 goes up, then P 4 would also go up thereby forcing the piston assembly up resulting in the lowering of the P 7 providing a self-correcting feature.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Control Of Fluid Pressure (AREA)
  • Fluid-Driven Valves (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Details Of Valves (AREA)
  • Feeding Of Articles By Means Other Than Belts Or Rollers (AREA)
  • Braking Systems And Boosters (AREA)
  • Electron Tubes For Measurement (AREA)
  • Stored Programmes (AREA)
  • Fluid-Pressure Circuits (AREA)
US06/922,521 1986-10-24 1986-10-24 Vacuum controller Expired - Lifetime US4795131A (en)

Priority Applications (14)

Application Number Priority Date Filing Date Title
US06/922,521 US4795131A (en) 1986-10-24 1986-10-24 Vacuum controller
IT4816487A IT1218140B (it) 1986-10-24 1987-07-10 Regolatore di vuoto
AU75987/87A AU588706B2 (en) 1986-10-24 1987-07-21 Vacuum controller
FI873301A FI85621C (fi) 1986-10-24 1987-07-29 Vakuumkontrollanordning.
NL8701851A NL8701851A (nl) 1986-10-24 1987-08-06 Onderdrukregelaar.
JP20940487A JPH073270B2 (ja) 1986-10-24 1987-08-25 真空調整器
CA 545528 CA1290308C (en) 1986-10-24 1987-08-27 Vacuum controller
DE19873733673 DE3733673C2 (de) 1986-10-24 1987-10-05 Unterdruckregler
AT267687A AT389178B (de) 1986-10-24 1987-10-09 Unterdruckregler zum regeln des unterdruckes in einem unterdrucksystem
FR8714252A FR2609563B1 (fr) 1986-10-24 1987-10-15 Dispositif de regulation de depression, notamment pour caisse aspirante de machine de fabrication du papier
SE8704084A SE467546B (sv) 1986-10-24 1987-10-21 Anordning foer styrning av undertrycket
BE8701208A BE1001002A5 (fr) 1986-10-24 1987-10-23 Dispositif de regulation de depression, notamment pour caisse aspirante de machine de fabrication du papier.
NO874427A NO172004C (no) 1986-10-24 1987-10-23 Vakuumregulator
GB8724876A GB2197935C (en) 1986-10-24 1987-10-23 Vacuum controller

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US06/922,521 US4795131A (en) 1986-10-24 1986-10-24 Vacuum controller

Publications (1)

Publication Number Publication Date
US4795131A true US4795131A (en) 1989-01-03

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Application Number Title Priority Date Filing Date
US06/922,521 Expired - Lifetime US4795131A (en) 1986-10-24 1986-10-24 Vacuum controller

Country Status (14)

Country Link
US (1) US4795131A (no)
JP (1) JPH073270B2 (no)
AT (1) AT389178B (no)
AU (1) AU588706B2 (no)
BE (1) BE1001002A5 (no)
CA (1) CA1290308C (no)
DE (1) DE3733673C2 (no)
FI (1) FI85621C (no)
FR (1) FR2609563B1 (no)
GB (1) GB2197935C (no)
IT (1) IT1218140B (no)
NL (1) NL8701851A (no)
NO (1) NO172004C (no)
SE (1) SE467546B (no)

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US5456286A (en) * 1993-08-17 1995-10-10 A. W. Chesterton Co. Shaft seal coolant flow control
US5762316A (en) * 1995-10-04 1998-06-09 Kraft Foods, Inc. Valve mechanism with improved sealing
US6082405A (en) * 1996-07-09 2000-07-04 Tac Ab Valve cone, a valve and a valve manufacturing process
US6446834B2 (en) * 1998-06-18 2002-09-10 Terrence Robert Davis Dispensing means
US6510867B2 (en) * 1999-09-03 2003-01-28 Lafleur Petroleum Services, Inc. Pressure relief valve
US20030116204A1 (en) * 2001-12-26 2003-06-26 Fsi International, Inc. High flow high control valve and assembly
US6609697B2 (en) * 2001-09-06 2003-08-26 Robert Andreas Gsteu Vacuum control valve
US20040000654A1 (en) * 2002-06-28 2004-01-01 Erickson Irving C. Precision modulating globe valve
US20070040134A1 (en) * 2003-05-26 2007-02-22 A/S Servo valve for a vacuum system
US20120211096A1 (en) * 2011-02-21 2012-08-23 Maxchip Electronics Corp. Check valve and vacuum system
WO2013108015A1 (en) * 2012-01-18 2013-07-25 Babcock Integrated Technology Limited A flood control valve assembly
US20150027557A1 (en) * 2011-07-08 2015-01-29 Fmc Technologies, Inc. Electronically controlled pressure relief valve
US20170114903A1 (en) * 2015-10-23 2017-04-27 Culligan International Company Control valve for fluid treatment apparatus
US11513540B2 (en) * 2017-07-19 2022-11-29 Imi Hydronic Engineering, Inc. Pressure compensated flow controller with only two pressures

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US2459527A (en) * 1945-12-27 1949-01-18 Oliver United Filters Inc Valve for overflow systems
US2861587A (en) * 1955-11-25 1958-11-25 Westinghouse Air Brake Co Vent valve device
DE1052765B (de) * 1956-05-02 1959-03-12 Karl Laux Absperrventil, insbesondere fuer Beregnungsanlagen, mit Antrieb durch das auf einen Kolben wirkende abzusperrende Mittel
US3063461A (en) * 1960-05-25 1962-11-13 Rudolph Hans Valve for use in respiratory and similar equipment
US3256903A (en) * 1961-11-21 1966-06-21 Ingeniors N Fliesberg Ab Fa Vacuum regulator
US3468341A (en) * 1964-11-19 1969-09-23 Broughton Corp Precision vacuum controller
US3332440A (en) * 1965-03-19 1967-07-25 Robertshaw Controls Co Sequentially-actuated multiplefunction control valve
US3463188A (en) * 1965-10-23 1969-08-26 St Louis Diecasting Corp Shot speed control valve and method of controlling the speed of a shot cylinder ram
US3508577A (en) * 1967-04-05 1970-04-28 Pan American Petroleum Corp Blowout control valve for drilling well
US3426998A (en) * 1967-05-25 1969-02-11 Kinwell Dev Co Piston valve with o-ring seal retained by split ring
US3590848A (en) * 1967-08-11 1971-07-06 Fliesberg Ingf Ab Regulator for maintaining within a restricted space a constant pressure which is lower than the ambient pressure
US3766933A (en) * 1970-07-27 1973-10-23 Broughton Corp Rolling diaphragm vacuum control
US3809127A (en) * 1971-12-03 1974-05-07 Us Navy Two position liquid flow control valve
US3822819A (en) * 1972-07-10 1974-07-09 S Wilson Fastener driving tool with improved valve
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US5456286A (en) * 1993-08-17 1995-10-10 A. W. Chesterton Co. Shaft seal coolant flow control
US5992819A (en) * 1994-02-10 1999-11-30 Abb Research Ltd. Arrangement in a valve actuator
WO1995022026A1 (en) * 1994-02-10 1995-08-17 Abb Research Ltd Arrangement in a valve actuator
US5762316A (en) * 1995-10-04 1998-06-09 Kraft Foods, Inc. Valve mechanism with improved sealing
US6082405A (en) * 1996-07-09 2000-07-04 Tac Ab Valve cone, a valve and a valve manufacturing process
US6446834B2 (en) * 1998-06-18 2002-09-10 Terrence Robert Davis Dispensing means
US6510867B2 (en) * 1999-09-03 2003-01-28 Lafleur Petroleum Services, Inc. Pressure relief valve
US6609697B2 (en) * 2001-09-06 2003-08-26 Robert Andreas Gsteu Vacuum control valve
US6807984B2 (en) 2001-12-26 2004-10-26 Fsi International, Inc. High flow high control valve and assembly
US20030116204A1 (en) * 2001-12-26 2003-06-26 Fsi International, Inc. High flow high control valve and assembly
US20040000654A1 (en) * 2002-06-28 2004-01-01 Erickson Irving C. Precision modulating globe valve
US6926249B2 (en) * 2002-06-28 2005-08-09 Invensys Building Systems, Inc. Precision modulating globe valve
US20070040134A1 (en) * 2003-05-26 2007-02-22 A/S Servo valve for a vacuum system
US7762520B2 (en) 2003-05-26 2010-07-27 Danfoss A/S Servo valve for a vacuum system
US20120211096A1 (en) * 2011-02-21 2012-08-23 Maxchip Electronics Corp. Check valve and vacuum system
US9915373B2 (en) * 2011-07-08 2018-03-13 Fmc Technologies, Inc. Electronically controlled pressure relief valve
US20150027557A1 (en) * 2011-07-08 2015-01-29 Fmc Technologies, Inc. Electronically controlled pressure relief valve
WO2013108015A1 (en) * 2012-01-18 2013-07-25 Babcock Integrated Technology Limited A flood control valve assembly
US20170114903A1 (en) * 2015-10-23 2017-04-27 Culligan International Company Control valve for fluid treatment apparatus
US10612670B2 (en) * 2015-10-23 2020-04-07 Culligan International Company Control valve for fluid treatment apparatus
US11022222B2 (en) 2015-10-23 2021-06-01 Culligan International Company Control valve for fluid treatment apparatus
US11365814B2 (en) 2015-10-23 2022-06-21 Culligan International Company Control valve for fluid treatment apparatus
US11513540B2 (en) * 2017-07-19 2022-11-29 Imi Hydronic Engineering, Inc. Pressure compensated flow controller with only two pressures

Also Published As

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GB2197935C (en) 1995-09-27
NO172004B (no) 1993-02-15
BE1001002A5 (fr) 1989-06-06
JPS63199983A (ja) 1988-08-18
FI873301A0 (fi) 1987-07-29
GB8724876D0 (en) 1987-11-25
DE3733673C2 (de) 1999-03-04
SE8704084D0 (sv) 1987-10-21
SE467546B (sv) 1992-08-03
AU588706B2 (en) 1989-09-21
IT1218140B (it) 1990-04-12
FR2609563B1 (fr) 1994-07-01
SE8704084L (sv) 1988-04-25
IT8748164A0 (it) 1987-07-10
CA1290308C (en) 1991-10-08
NL8701851A (nl) 1988-05-16
AU7598787A (en) 1988-04-28
DE3733673A1 (de) 1988-06-16
AT389178B (de) 1989-10-25
ATA267687A (de) 1989-03-15
FI85621C (fi) 1992-05-11
GB2197935B (en) 1991-04-17
NO172004C (no) 1993-05-26
GB2197935A (en) 1988-06-02
NO874427D0 (no) 1987-10-23
FR2609563A1 (fr) 1988-07-15
JPH073270B2 (ja) 1995-01-18
FI873301A (fi) 1988-04-25
FI85621B (fi) 1992-01-31
NO874427L (no) 1988-04-25

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